CN101052819A - Dual-action clutch system - Google Patents
Dual-action clutch system Download PDFInfo
- Publication number
- CN101052819A CN101052819A CNA2005800378955A CN200580037895A CN101052819A CN 101052819 A CN101052819 A CN 101052819A CN A2005800378955 A CNA2005800378955 A CN A2005800378955A CN 200580037895 A CN200580037895 A CN 200580037895A CN 101052819 A CN101052819 A CN 101052819A
- Authority
- CN
- China
- Prior art keywords
- clutch
- dual
- piston
- radially
- action
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
- F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
- F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
- F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
- F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D21/00—Systems comprising a plurality of actuated clutches
- F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
- F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D25/00—Fluid-actuated clutches
- F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D21/00—Systems comprising a plurality of actuated clutches
- F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
- F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
- F16D2021/0661—Hydraulically actuated multiple lamellae clutches
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
The invention relates to a dual clutch system (20) for a dual clutch transmission (14) for motor vehicles. Said system comprises a first and a section friction clutch (28, 30), both fluidically actuated, a first piston system used to actuate the first friction clutch (28), and a first piston (70), a first piston chamber (72) and a first centrifugal force compensating chamber (78), a second piston system used to actuate the second friction clutch (30) and a second piston (90), a second piston chamber (92) and a second centrifugal force compensating chamber (86). The piston chambers (72, 92) and the centrifugal force compensating chambers (78, 86) are arranged on opposite sides of the pistons (70, 90) associated therewith and are connected to a valve system via feed lines (74, 82, 94). The invention is characterized in that the centrifugal force compensating chambers are connected to the valve system via a common line. Alternatively, the input element (68) of the radially inner clutch (30) is the inner disk support (68).
Description
Technical field
The present invention relates to a kind of dual-action clutch system that is used for the double-action clutch transmission device of motor vehicle, have first friction clutch and second friction clutch of equal fluid-activatable; The first piston system, it is used to activate first friction clutch and has first piston, first piston space and the first centrifugal force equalization space; Second piston system, it is used to activate second friction clutch and has second piston, second piston space and the second centrifugal force equalization space.Piston space and centrifugal force equalization space lay respectively on the opposite side of associated piston, and are connected with a valve system by intake line.
Background technique
The dual-action clutch system integral body of described type is known.
The double-action clutch transmission device has a dual-action clutch system and two part transmission devices.The part transmission device generally is designed to auxiliary shaft transmision gear.Here, one of them part transmission device is assigned to the even number gear stage, and another part transmission device is assigned to the odd number gear stage.
Therefore, can carry out gear shift by means of the overlap action of two clutches of dual-action clutch system, and need not interrupt tractive force.
The double-action clutch transmission device of described type is applicable to motor vehicle, is particularly useful for passenger vehicle.
Current fluid-operated friction clutch, for example multiplate clutch of wet type operation of in dual-action clutch system, generally using.
In order to obtain minor axis to design, usually these preferred two double-action clutchs radially cover another, one of them friction clutch radially is positioned at inside, and another radially is positioned at the outside.
For especially hydraulic oil of fluid is provided to friction clutch, knownly provide a kind of rotation lead-through with necked part, the public hub of two double-action clutchs is positioned on this necked part.
Here, in known dual-action clutch system, four conduits are located at respectively on rotation lead-through and the hub, and two pipes wherein are assigned to two piston spaces, and two pipes are assigned to two centrifugal force equalization spaces in addition.
Here, the catheter shaft in first piston space is positioned at an end to ground.Adjacent with it is the conduit of the first centrifugal force equalization space.And the conduit of second piston space is adjacent with this conduit, and axially is furnished with the conduit of the second centrifugal force equalization space at the other end.
Summary of the invention
The objective of the invention is to, a kind of improved dual-action clutch system is provided.
Described purpose realizes that by dual-action clutch system as described in the preamble wherein, the centrifugal force equalization space is connected with valve system by means of a public pipeline.
In a second aspect of the present invention, this purpose realizes by double-action clutch as described in the preamble, wherein, friction clutch is radially nested multiplate clutch, and have an interior plate rack and an outer plate rack respectively, the input element of radially outer multiplate clutch is outer plate rack, and the input element of radially inner clutch is interior plate rack.
By means of measure, can provide a kind of axial generally more compact dual-action clutch system, especially because need intake line still less to come to introduce fluid to piston space and fluid equalization space according to first aspect present invention.Also brought lightweight advantage thus.
Utilization can realize short length of installation equally, and bring lightweight advantage thus according to the dual-action clutch system of second aspect present invention.
In dual-action clutch system according to the present invention, advantageously, friction clutch has an input element respectively, and wherein input element is installed on the hub, and hub and drives input shaft and is connected and can not relatively rotates.
Described measure makes the axial arrangement compactness of dual-action clutch system on the whole.
Here, particularly advantageous is to drive input shaft and be connected with hub by means of a retainer that radially centers on friction clutch.
By means of described measure, can advantageously allow the driving output element of friction clutch near the driving input shaft, radially guide through hub.
According to another preferred embodiment, hub is installed in a rotation lead-through and is fixed on the necked part on the housing.
Therefore, can provide the fluid that makes its work to friction clutch via rotation lead-through and hub.
Here particularly advantageous is that hub has radial conduit, so that provide fluid to friction clutch.
Here also advantageously, hub has the conduit of at least two radial actuation, to activate two friction clutches.In this article, term " radial conduit " will be understood on wide sense.During with relevant rotation lead-through, longitudinal section generally is presumed to, and only can see the projection of a radial conduit or a radial conduit respectively in the expression radial conduit.But, self-evident, radial conduit for example also can be understood as a plurality of single conduits that upwards distribute in week, for example is the hole.In the context of the present invention, single radial conduit also can be understood like this, that is, two are connected at the single ring duct of the single conduit that upwards staggers in week with a rotation lead-through, but depart from each other radially outwardly in the axial direction.
The rotation lead-through preferably has a ring duct that forms two public pipelines of centrifugal force equalization space.
Here, particularly advantageous is that ring duct is arranged between the radial conduit of two actuatings vertically.
By means of described measure, ring duct and two centrifugal force equalization spaces can be coupled together, especially when the centrifugal force equalization space is adjacent to each other between two piston spaces vertically.
According to another preferred implementation, hub has at least one first subsidiary conduit radially, and it is connected with the first centrifugal force equalization space and at least one second subsidiary conduit radially, it is connected with the second centrifugal force equalization space, and wherein radially subsidiary conduit radially is connected with ring duct inner.
Here, on the one hand, radially subsidiary conduit can be made up of conduit radially outward branch, interconnection in all cases respectively.But, preferred first radially subsidiary conduit and second radially subsidiary conduit upwards stagger relative to each other in week.Only a radial conduit can be seen in the projection that makes progress in week, so, in the case, for the sake of simplicity, sometimes just be called " one " radially subsidiary conduit.
Here, also particularly advantageous is that the input element of one of friction clutch radially is connected with hub in the zone between the subsidiary conduit at two.
In this way, the input element of described friction clutch can be used as two dividing elements between the centrifugal force equalization space.The preferably radially inner friction clutch of the friction clutch that its input element is connected with hub in this way.
According to another preferred embodiment, ring duct is used for providing cooling liquid at least one friction clutch.
According to another preferred embodiment, centrifugal force equalization space fluid each other connects.
The centrifugal force equalization space generally always is in passive state, that is to say, is provided non-pressurized fluid, and for example, if clutch activates by pressure fluid is introduced in the associated piston space, fluid just is being actuated and is flowing out relevant centrifugal force equalization space.If two centrifugal force equalization space fluid connections each other, this is just more easy.Especially, in rotation lead-through and/or hub, need not complicated conduit system.
But, also can imagine usually, under the adjacent situation of centrifugal force equalization space, for example by means of the opening in the dividing element (such as the input element in the radially inner friction clutch) by the centrifugal force equalization space each other fluid connect.
According to preferred embodiment a kind of, friction clutch is radially nested multiplate clutch, or with a multiplate clutch that is arranged in another, and have an interior plate rack and an outer plate rack respectively.
In described embodiment, especially advantageously, the input element of radially outer multiplate clutch is its outer plate rack, and the input element of radially inner clutch is a plate rack in it.
In this way, just can adopt simple mode on the structure, make on the dual-action clutch system overall axial very short.
Self-evident, above-mentioned feature and the feature that will set forth below not only can be used in the assembled scheme of appointment respectively, also can be used in other combination or use individually, and do not depart from the scope of the present invention.
Description of drawings
One exemplary embodiment of the present invention is shown in the drawings and be described in more detail in the following description.In the accompanying drawings:
Fig. 1 shows according to the schematic longitudinal elevation view of the dual-action clutch system of one embodiment of the invention (rotational symmetric substantially system partly cut open figure), is combined with the associated components of double-action clutch transmission device;
Fig. 2 shows the longitudinal section of the hub of dual-action clutch system shown in Figure 1.
Embodiment
In Fig. 1, whole with 10 power trains of representing motor vehicle.
Power train 10 has the internal-combustion engine 12 that schematically shows, and its output terminal is connected with double-action clutch transmission device 14.
Power train 10 is specially adapted to motor vehicle.The motor of driving machine motor vehicle can be an internal-combustion engine 12, or any other desirable drive motor for example power driver, hybrid drive etc.
Double-action clutch transmission device 14 comprises a multi-range transmission (schematically representing with 16 in the drawings), and it is designed to an auxiliary shaft transmision gear and comprises two part transmission devices.
In addition, double-action clutch transmission device 14 has dual-action clutch system 20, and its input end is connected with the output terminal of internal-combustion engine 12, and it is connected with multi-range transmission 16 at output terminal.
Or rather, dual-action clutch system 20 has input shaft 22, and by means of meshing engagement structure etc., this input shaft can be connected and can not relatively rotate with the driving output shaft of internal-combustion engine 12.
Dual-action clutch system 20 also has first output shaft 24 of solid shaft form, and it is connected with first portion's transmission device of multi-range transmission 16.In addition, dual-action clutch system 20 has second output shaft 26 of quill shaft form, and it is connected with the second portion transmission device.Axle 24,26 is arranged concentric relative to each other.
Dual-action clutch system 20 has first friction clutch 28, and it connects the output shaft 22 and first output shaft 24, also has second friction clutch 30, and it connects the output shaft 22 and second output shaft 26.
Two friction clutches 28,30 are radially nested, and wherein first friction clutch 28 radially is positioned at the outside, and second friction clutch 30 radially is positioned at the inboard with it with one heart.
Two friction clutches 28,30 are fixed in the retainer 32, and this retainer 32 is connected with input shaft 22.Or rather, retainer 32 has the first retainer part 34, and it is connected with input shaft 22 and extends from input shaft 22 radially outwardly.In addition, retainer 32 has the second retainer part 36, and it is connected and can not relatively rotates and have one on the first retainer part 34 as the circular cylinder shaped portion of outer plate rack 38 forms of first friction clutch 28 and the local part that extends radially inwardly.
The interior plate rack 40 of first friction clutch 28 is connected with first basket support 42, and this first basket support 42 and the first retainer part 34 are close to, and are connected with first output shaft 24 by means of first meshing engagement structure 44.
The outer plate rack 46 of second friction clutch 30 is connected with second basket support 48.Second basket support 48 and first basket support 42 are directly contiguous, and are connected with second output shaft 26 (quill shaft) by means of second meshing engagement structure 50.
In figure schematically illustrated, cod can be arranged between the first retainer part 34 and first basket support 42 and between first basket support 42 and second basket support 48.
In the drawings, clutch-pedal support of 60 expressions, it is fixed on the housing, that is to say and does not rotate.In addition, 58 have schematically shown a valve system or a hydraulic control system, by means of it, can handle dual-action clutch system.
Clutch-pedal support 60 tightens an intrinsic rotation drawing-in system 62, and it has axially outstanding hollow axle journal (spigot) part 64, and this necked part is arranged with one heart around two output shafts 24,26.Necked part 64 axially extends from the side of the second retainer part 36, almost as far as second basket support 48 that is connected with second output shaft 26.Here, necked part 64 radially is positioned at two friction clutches 28,30.
Hub 66 is rotatably installed on the necked part 64 of rotation drawing-in system 62.There is shown two bearings, hub 66 is rotatably installed on the necked part 64 of rotation drawing-in system 62 by means of it.
The second retainer part 36 is rigidly connected with hub 66, so hub 66 just forms the input element of dual-action clutch system 20, and with the rotational speed rotation of attached motor 22.
The interior plate rack 68 of second friction clutch 30 is fixed on the hub 66.
The first piston 70 of first friction clutch 28 is installed between the interior plate rack 68 and the second retainer part 36, so first piston 70 just can axially move with respect to hub 66.Piston 70 is for disc shaped designs, and loose boss 66 extend radially outwardly as far as first friction clutch 28.
First piston space 72 is formed between the second retainer part 36 and the first piston 70.First piston space 72 is connected with valve system 58 with clutch-pedal support 60 by means of rotation drawing-in system 62.By (generally being hydraulic fluid with fluid, as ATF oil) supply in the first piston space 72 (via the first radial actuation conduit 74, as described below), first piston 70 axially moves with respect to the second retainer part 36, and the multi-disc of first friction clutch 28 is forced together, so described multi-disc is with regard to frictional engagement, so that closed thus first the friction clutch 28 and input shaft 22 and first output shaft 24 coupled together.
Opening state by first friction clutch 28 is carried out in a controlled manner to the transition energy of closed state, thereby produces a suitable slippage stage, so that allow the starting and the gear shift of no ballistic kick thus respectively.
Supply with the purpose of hydraulic fluid for giving first piston space 72, the first radial actuation conduit 74 (for example forming by means of a plurality of holes of upwards staggering in week) is arranged in the hub 66, this first radial actuation conduit 74 couples together first ring duct (any details in the drawings be not shown) of first piston space 72 with corresponding necked part 64, wherein, first ring duct is connected with clutch-pedal support 60 or is connected with valve system 58 by means of suitable conduit in the rotation drawing-in system 62 again.
Also be formed with a web (any details is not shown in the drawings) on interior plate rack 68, a plurality of first Returnning springs 76 rest on this web, and these a plurality of first Returnning springs 76 are arranged like this, that is, and equably around circumferential distribution.The power that first piston 70 overcomes first Returnning spring 76 thus activates.
The first centrifugal force equalization space 78 is between the interior plate rack 68 of the piston 70 and second friction clutch 30.
Centrifugal force equalization space 78 has the function that produces clutch actuation force reaction power, clutch actuation power be produce by centrifugal force and result from the relevant first piston space 72.
The hydraulic fluid that exists in the first piston space 72 is especially extrapolated with high rotation speed, thereby finally on the direction of actuation of first friction clutch 28 active force is put on piston.Therefore, when first friction clutch 28 was opened, described active force reacted on the opposite force that is applied by Returnning spring 76 in the mode of interfering edge.For equilibrium described " interfering edge ", allow that hydraulic fluid does not flow in the relative centrifugal force equalization space 78 with pressurizeing.Because centrifugal force produces resistivity on the opening direction of first friction clutch 28, it reacts on described " interfering edge " and cancels each other with it.
For this reason, the first centrifugal force equalization space 78 by means of first radially subsidiary conduit 80 be connected with second ring duct 82 on the necked part 64, and second ring duct 82 is connected with valve system 58 by means of corresponding conduit or pipeline in the rotation drawing-in system 62.
The opposite side of plate rack 68 in the second centrifugal force equalization space 86 is built up in.The described second centrifugal force equalization space 86 by means of second radially subsidiary conduit 84 be connected with second ring duct 82 of necked part 64.
Therefore, two centrifugal force equalization spaces 78,86 are adjacent one another are, and only the interior plate rack 68 by second friction clutch 30 separates each other.
The second centrifugal force equalization space 86 is defined in axial opposite side by second piston 90, and this second piston 90 is installed into removable in the axial direction with respect to hub 66 equally.
Supporting element 89 is fastened on the hub 66.Described supporting element 89 radially axially stretches out between second piston 90 and second basket support 48.Second piston space 92 is built up between the supporting element 89 and second piston 90.Second piston space 92 is connected with the 3rd ring duct on the necked part 64 by means of the second radial actuation conduit 94.Second piston space 92 is connected with valve system 58 by means of described the 3rd ring duct.
In addition, second Returnning spring 96 is arranged in the second centrifugal force equalization space 86, and this second Returnning spring 96 rests on the bearing element 88.In bearing element 88 rests on again on the free end of plate rack 68 or fixed thereon.Bearing element 88 also is used for defining the second centrifugal force equalization space 86 by means of the Sealing between the bearing element 88 and second piston 90.
The function of second friction clutch 30 is corresponding with first friction clutch 28, and only the direction of actuation location in the opposite direction.When first piston 70 was arranged in two friction clutches, 28,30 1 sides, second piston 90 was arranged in opposite side.Second piston 90 is similarly a disc shaped element, and it is installed in the axial middle section of second friction clutch 30 on the hub 66.Second piston 90 radially extends from described axial middle section around second friction clutch 30.The second centrifugal force equalization space 86 substantially radially is arranged in second friction clutch 30 thus.Second Returnning spring 96 also radially is arranged in second friction clutch 30.
As the result of described measure, dual-action clutch system 20 can be totally compact especially in the axial direction.
This also is easy, because two centrifugal force equalization spaces 78,86 are arranged to adjacent one another are, and can be connected with valve system 58 by means of second ring duct 82 on the necked part 64 of rotation drawing-in system 62, that is to say, can finally be supplied to non-pressurized hydraulic fluid via single conduit (public pipeline).
Friction clutch 28,30 also can be supplied to cooling liquid via second ring duct 82 or via the staggered radially subsidiary conduit that makes progress in week.Described cooling liquid is because centrifugal force radially outwards flows out the through hole in the plate rack for example, and cools off two friction clutches 28,30.Cooling liquid is returned (generally via cooler) therefrom.
Returnning spring 76,96 is shown helical spring in the drawings.But, also can use the sheet spring instead.
Especially significantly be only to need three axial grooves that stagger in the axial direction (ring duct) on the necked part 64 of rotation drawing-in system 62, so that hydraulic fluid is presented to dual-action clutch system 20.This has also just shortened axial length of installation, and has brought lightweight advantage.
In order to activate friction clutch 28,30, for example the hydraulic fluid under 15 bar pressures imports respectively in the corresponding piston space 72 and 92.
Although the hub shown in the figure 66 has radially subsidiary conduit 80,84 of one first radial actuation conduit 74, second radial actuation conduit 94 and two respectively, and is self-evident, can arrange that corresponding conduit or hole are with the circumferential distribution around hub 66.
The aperture of conduit 80 is to vertically moving towards; The aperture of conduit 84 is to the tiltedly trend that leans outward.
An axial pipeline 101 is externally led in the hole of the conduit 84,94 of clutch 30 in all cases.The axial pipeline 103 that is upwards staggering in week is led in the hole of conduit 80,74 accordingly respectively.
Claims (14)
1, a kind of dual-action clutch system (20) that is used for the double-action clutch transmission device (14) of motor vehicle has:
First friction clutch and second friction clutch (28,30) of equal fluid-activatable,
The first piston system, it is used to activate first friction clutch (28) and has first piston (70), first piston space (72) and the first centrifugal force equalization space (78),
Second piston system, it is used to activate second friction clutch (30) and has second piston (90), second piston space (92) and the second centrifugal force equalization space (86),
Piston space (72,92) and centrifugal force equalization space (78,86) lay respectively on the opposite side of associated piston (70,90), and are connected with a valve system by means of intake line (74,82,94),
It is characterized in that centrifugal force equalization space (78,86) is connected with this valve system by means of a public pipeline (82).
2, dual-action clutch system as claimed in claim 1, it is characterized in that, described friction clutch (28,30) has an input element (38 respectively, 68), this input element (38,68) is installed on the hub (66), and this hub (66) and drives input shaft (22) and is connected and can not relatively rotates.
3, dual-action clutch system as claimed in claim 2 is characterized in that, this drives input shaft (22) and is connected with hub (66) by means of a retainer (32) that radially centers on friction clutch (28,30).
As claim 2 or 3 described dual-action clutch systems, it is characterized in that 4, this hub (66) is installed on the necked part (64) of a rotation drawing-in system (62), this necked part (64) is fixed on the housing.
5, dual-action clutch system as claimed in claim 4 is characterized in that, this hub (66) has radial conduit (74,80,84,94), supplies with fluid to friction clutch (28,30).
6, dual-action clutch system as claimed in claim 5 is characterized in that, this hub (66) has at least two radial actuation conduits (74,94) so that kinetic friction clutch (28,30).
As the described dual-action clutch system of one of claim 4 to 6, it is characterized in that 7, this rotation drawing-in system has ring duct (82), it forms the public pipeline (82) of two centrifugal force equalization spaces (78,86).
8, dual-action clutch system as claimed in claim 7, it is characterized in that, this hub (66) has at least one first subsidiary conduit (80) radially, it is connected with the first centrifugal force equalization space (78), with at least one second subsidiary conduit (84) radially, it is connected with the second centrifugal force equalization space (86), and wherein radially subsidiary conduit (80,84) radially is connected with ring duct (82) inner.
9, dual-action clutch system as claimed in claim 8 is characterized in that, the input element (68) of one of this friction clutch (28,30) (30) radially is connected with hub (66) in the zone between the subsidiary conduit (80,84) at two.
As the described dual-action clutch system of one of claim 6 to 9, it is characterized in that 10, this ring duct (82) also is used for supplying with cooling liquid at least one friction clutch (28,30).
As the described dual-action clutch system of one of claim 1 to 10, it is characterized in that 11, this centrifugal force equalization space (78,86) fluid each other connects.
12, as the described dual-action clutch system of one of claim 1 to 11, it is characterized in that described friction clutch (28,30) be radially nested multiplate clutch (28,30), and have an interior plate rack (40 respectively, 68) and an outer plate rack (38,46).
13, dual-action clutch system as claimed in claim 12, it is characterized in that, the input element (38) of this radially outer multiplate clutch (28) is outer plate rack (38), and the input element (68) of radially inner clutch (30) is interior plate rack (68).
14, dual-action clutch system as claimed in claim 1, described friction clutch (28,30) be radially nested multiplate clutch (28,30), and have an interior plate rack (40 respectively, 68) and an outer plate rack (38,46), it is characterized in that the input element (38) of this radially outer multiplate clutch (28) is outer plate rack (38), and the input element (68) of radially inner clutch (30) is interior plate rack (68).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102004055361.0 | 2004-11-05 | ||
| DE102004055361A DE102004055361B4 (en) | 2004-11-05 | 2004-11-05 | Dual clutch assembly |
| PCT/EP2005/011519 WO2006048179A1 (en) | 2004-11-05 | 2005-10-27 | Dual clutch system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101052819A true CN101052819A (en) | 2007-10-10 |
| CN101052819B CN101052819B (en) | 2010-07-28 |
Family
ID=35520727
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2005800378955A Active CN101052819B (en) | 2004-11-05 | 2005-10-27 | Dual-action clutch system |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US7648012B2 (en) |
| EP (1) | EP1807636B1 (en) |
| JP (1) | JP4722937B2 (en) |
| CN (1) | CN101052819B (en) |
| DE (2) | DE102004055361B4 (en) |
| WO (1) | WO2006048179A1 (en) |
Cited By (21)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101725645A (en) * | 2008-10-29 | 2010-06-09 | 株式会社F.C.C. | Multiple disc clutch apparatus |
| CN101983293A (en) * | 2007-12-06 | 2011-03-02 | 谢夫勒科技有限两合公司 | Multiple clutch device |
| CN102003526A (en) * | 2009-08-26 | 2011-04-06 | 通用汽车环球科技运作公司 | Actuation device having wiper seals for a dual clutch transmission |
| CN102155535A (en) * | 2009-08-26 | 2011-08-17 | 通用汽车环球科技运作有限责任公司 | Actuation device for a dual clutch transmission |
| CN103140696A (en) * | 2010-07-29 | 2013-06-05 | 舍弗勒技术股份两合公司 | Clutch device |
| CN103591280A (en) * | 2012-08-14 | 2014-02-19 | 通用汽车环球科技运作有限责任公司 | Transmission clutch piston compensator feed circuit |
| CN103775531A (en) * | 2012-10-17 | 2014-05-07 | 舍弗勒技术股份两合公司 | Inline clutch with intermediate web |
| CN103797263A (en) * | 2011-07-29 | 2014-05-14 | 现代派沃泰有限公司 | Dual Clutch Device |
| CN103836091A (en) * | 2012-11-20 | 2014-06-04 | 博格华纳公司 | Dual clutch device and method for mounting the same |
| CN103883637A (en) * | 2012-12-20 | 2014-06-25 | 舍弗勒技术股份两合公司 | Clutch device |
| CN104033589A (en) * | 2013-03-04 | 2014-09-10 | 格特拉格传动机构和齿轮工厂赫尔曼·哈根迈尔有限公司&两合公司 | Control Method For Dual-clutch Transmission |
| CN104053922A (en) * | 2012-01-20 | 2014-09-17 | 舍弗勒技术有限两合公司 | Wet Friction Clutch With Integrated Damping System |
| CN104061254A (en) * | 2013-03-21 | 2014-09-24 | 舍弗勒技术有限两合公司 | Rotation Component, Engaged Part Of Two Rotation Components And Method For Manufacturing Rotation Component |
| CN105090267A (en) * | 2014-05-22 | 2015-11-25 | 舍弗勒技术股份两合公司 | Clutch assembly |
| CN105526278A (en) * | 2014-10-16 | 2016-04-27 | 美国轮轴制造公司 | Dual piston actuator |
| CN106499742A (en) * | 2015-09-03 | 2017-03-15 | 舍弗勒技术股份两合公司 | Clutch device |
| CN107461424A (en) * | 2016-06-03 | 2017-12-12 | Fca意大利股份公司 | Motor vehicle transmission with double clutch coupling arrangement |
| CN109931339A (en) * | 2017-12-18 | 2019-06-25 | 舍弗勒技术股份两合公司 | Clutch device, multiple clutch device, electric drive unit and drive assembly for a motor vehicle |
| CN112639321A (en) * | 2018-09-06 | 2021-04-09 | 法雷奥离合器公司 | Double clutch mechanism |
| CN113544400A (en) * | 2019-05-14 | 2021-10-22 | 舍弗勒技术股份两合公司 | Clutch device, hybrid module and drive device for a motor vehicle |
| CN114096757A (en) * | 2019-07-10 | 2022-02-25 | 舍弗勒技术股份两合公司 | Actuating device for a multi-plate brake and transmission comprising an actuating device and a multi-plate brake |
Families Citing this family (32)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| SE0501542L (en) | 2005-07-01 | 2006-07-25 | Itt Mfg Enterprises Inc | Pump for pumping contaminated liquid including solids |
| FR2890714B1 (en) * | 2005-09-15 | 2009-02-27 | Renault Sas | DEVICE FOR SUPPLYING THE COMPENSATION CHAMBERS OF A DOUBLE CLUTCH |
| DE102006010113C5 (en) * | 2006-02-28 | 2010-05-20 | Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg | Dual clutch arrangement for a dual-clutch transmission |
| DE102007009964A1 (en) * | 2006-03-22 | 2007-09-27 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Coupling gear for power transmission between rotatory drive unit and rotatory propelled unit, has two bearings among which former is connected with front part of coupling gear and latter bearing is connected with cover |
| DE102007058854A1 (en) | 2007-12-06 | 2009-06-10 | Schaeffler Kg | Multiple clutch arrangement for a double clutch in a vehicle comprises a bearing unit with a ball bearing |
| DE102007058853A1 (en) | 2007-12-06 | 2009-07-16 | Schaeffler Kg | Multiple clutch device, particularly double clutch device, has two friction clutch arrangements with friction torque transmitting friction element carriers, which are connected with friction element of friction clutch arrangement |
| DE102007058863A1 (en) | 2007-12-06 | 2009-06-10 | Schaeffler Kg | Multiple clutch device, particularly double clutch device, has two friction clutch arrangements arranged in radial direction in overlapping manner having torque-transferring friction element carriers |
| DE102008008062B4 (en) * | 2008-02-01 | 2014-05-22 | Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg | Dual clutch assembly |
| DE102009006649B4 (en) * | 2008-02-11 | 2021-06-17 | Schaeffler Technologies AG & Co. KG | Double clutch arrangement |
| DE102008055682C5 (en) | 2008-10-28 | 2017-11-02 | Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg | Double clutch with upright piston and improved engagement bearings |
| DE102008055681B4 (en) * | 2008-10-28 | 2020-10-15 | Magna Pt B.V. & Co. Kg | Double clutch arrangement for a double clutch transmission |
| DE102009001286B4 (en) | 2009-03-03 | 2019-10-24 | Zf Friedrichshafen Ag | Multiple coupling device, in particular dual clutch device, with a rotating with an external transmission input shaft pressure medium supply element |
| DE102009039223B8 (en) * | 2009-08-28 | 2013-05-08 | Getrag Ford Transmissions Gmbh | Dual clutch arrangement for a transmission with two input shafts |
| US8453819B2 (en) | 2010-02-22 | 2013-06-04 | Twin Disc, Inc. | Balanced clutch system |
| DE102011004467A1 (en) | 2011-02-21 | 2012-08-23 | Zf Friedrichshafen Ag | Method and device for controlling switching elements of an automatic transmission with automatic start-stop |
| US8844695B2 (en) * | 2011-02-24 | 2014-09-30 | Ford Global Technologies, Llc | Carrying fluid to balance dams in a servo piston support |
| EP2732174B1 (en) | 2011-07-15 | 2017-08-09 | Schaeffler Technologies AG & Co. KG | Dual clutch |
| CN103765029B (en) | 2011-08-11 | 2016-11-09 | 舍弗勒技术股份两合公司 | Stator for friction clutch |
| KR101610085B1 (en) | 2011-09-22 | 2016-04-08 | 현대자동차 주식회사 | Hydraulic clutch |
| KR101566725B1 (en) * | 2011-09-27 | 2015-11-09 | 현대자동차 주식회사 | Hydraulic clutch |
| US8613682B2 (en) * | 2012-05-04 | 2013-12-24 | GM Global Technology Operations LLC | Rotating clutch balance fill system |
| DE102012013873B4 (en) | 2012-07-12 | 2019-03-28 | GETRAG B.V. & Co. KG | A disc carrier bearing assembly and clutch assembly for a motor vehicle powertrain |
| US8967351B2 (en) * | 2012-08-14 | 2015-03-03 | Gm Global Technology Operations, Llc | Transmission clutch piston compensator feed circuit |
| DE102012021074B4 (en) * | 2012-10-19 | 2016-05-04 | Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg | Method for operating a hybrid drive train |
| DE202013009459U1 (en) | 2013-10-28 | 2015-01-29 | Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg | Hub arrangement for motor vehicle clutch |
| DE102014225143A1 (en) * | 2014-12-08 | 2016-06-09 | Federal-Mogul Sealing Systems Gmbh | Clutch balance piston |
| WO2017129165A1 (en) * | 2016-01-29 | 2017-08-03 | Schaeffler Technologies AG & Co. KG | Clutch arrangement and drive train for a motor vehicle |
| WO2019002375A1 (en) * | 2017-06-28 | 2019-01-03 | Valeo Embrayages | Clutch module for a motor vehicle |
| FR3068426B1 (en) * | 2017-06-28 | 2019-08-23 | Valeo Embrayages | CLUTCH MODULE FOR MOTOR VEHICLE |
| DE102018000565A1 (en) | 2018-01-24 | 2019-07-25 | Borgwarner Inc. | Coupling device and drive train with such a coupling device |
| KR102076345B1 (en) * | 2018-04-20 | 2020-02-11 | 주식회사 카펙발레오 | Dual clutch device for vehicle |
| DE102021203150B3 (en) | 2021-03-29 | 2022-09-01 | Magna Pt B.V. & Co. Kg | multiple clutch assembly |
Family Cites Families (22)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0781594B2 (en) * | 1985-08-31 | 1995-08-30 | 三菱自動車工業株式会社 | Power transmission device |
| US4741422A (en) * | 1987-03-09 | 1988-05-03 | General Motors Corporation | Clutch assembly with a pressure balance chamber |
| US6021879A (en) * | 1999-04-05 | 2000-02-08 | General Motors Corporation | Rotating clutch balance apparatus |
| DE10004179C5 (en) * | 1999-09-30 | 2017-06-29 | Volkswagen Ag | Multiple clutch device |
| JP2001263369A (en) * | 2000-03-21 | 2001-09-26 | Aisin Seiki Co Ltd | Clutch device for automatic transmission |
| EP1195537B1 (en) * | 2000-10-05 | 2003-03-12 | Ford Global Technologies, Inc., A subsidiary of Ford Motor Company | Transmission double clutch with two input shafts |
| DE10102874A1 (en) * | 2000-11-17 | 2002-06-06 | Zf Sachs Ag | coupling system |
| WO2002040886A1 (en) * | 2000-11-17 | 2002-05-23 | Mannesmann Sachs Ag | Clutch system |
| DE10133638A1 (en) * | 2001-07-11 | 2003-01-30 | Zf Sachs Ag | Multiple coupling device, in particular double coupling device |
| WO2003006839A2 (en) * | 2001-07-11 | 2003-01-23 | Zf Sachs Ag | Multiple clutch system comprising two clutch configurations which can be coupled in such a way that they commonly rotate |
| DE10163404B4 (en) * | 2001-12-21 | 2009-06-04 | Zf Sachs Ag | Method for controlling a clutch system with at least one multi-disc clutch arrangement |
| DE10223780C1 (en) * | 2002-05-29 | 2003-10-16 | Porsche Ag | Gear shift mechanism, for an IC motor with a multiple hydraulic clutch, has a bearing flange around the gear housing opening as a support for the roller bearing between it and the clutch cage with the drive hub |
| DE20302464U1 (en) * | 2003-02-15 | 2004-07-01 | Friedr. Fingscheidt Gmbh | Headrest with adjustment mechanism |
| DE10323514A1 (en) * | 2003-05-24 | 2004-12-23 | Dr.Ing.H.C. F. Porsche Ag | Coupling device, in particular multi-plate clutch for a double clutch transmission |
| DE20320467U1 (en) * | 2003-07-23 | 2004-09-16 | Zf Friedrichshafen Ag | Arrangement of two adjacent multi-disk clutch units, supplied with coolant and/or lubricant directly by pressure compensating chamber |
| DE10333431A1 (en) * | 2003-07-23 | 2005-02-10 | Zf Friedrichshafen Ag | Arrangement of two adjacent multi-disk clutch units, supplied with coolant and/or lubricant directly by pressure compensating chamber |
| EP1521003B1 (en) * | 2003-09-30 | 2007-01-10 | BorgWarner Inc. | Oil management system for dual clutch transmissions |
| DE20320464U1 (en) | 2003-10-30 | 2004-08-26 | Zf Friedrichshafen Ag | Clutch unit in transmission has two axially and radially adjacent multi-plate clutches with plates of radially outer plate packet pressed axially against contact section of common plate carrier |
| DE102004013265A1 (en) * | 2004-03-18 | 2005-03-10 | Zahnradfabrik Friedrichshafen | Double clutch for automobile drive train with common centrifugal pressure equalization space between operating pistons for respective clutch mechanisms |
| EP1630440B1 (en) * | 2004-08-26 | 2008-04-09 | HOERBIGER Antriebstechnik GmbH | Hydraulic double clutch |
| US7246692B2 (en) * | 2004-10-26 | 2007-07-24 | Borgwarner Inc. | Dual clutch mechanism for a transmission |
| US7293637B2 (en) * | 2005-01-06 | 2007-11-13 | Ford Global Technologies, Inc. | Modular twin clutch transmission input for hybrid vehicle |
-
2004
- 2004-11-05 DE DE102004055361A patent/DE102004055361B4/en active Active
-
2005
- 2005-10-27 CN CN2005800378955A patent/CN101052819B/en active Active
- 2005-10-27 JP JP2007539509A patent/JP4722937B2/en active Active
- 2005-10-27 EP EP05807291A patent/EP1807636B1/en active Active
- 2005-10-27 WO PCT/EP2005/011519 patent/WO2006048179A1/en active Application Filing
- 2005-10-27 DE DE502005007588T patent/DE502005007588D1/en active Active
-
2007
- 2007-04-27 US US11/741,715 patent/US7648012B2/en not_active Expired - Fee Related
Cited By (43)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101983293B (en) * | 2007-12-06 | 2014-06-11 | 谢夫勒科技股份两合公司 | Multiple clutch device |
| CN101983293A (en) * | 2007-12-06 | 2011-03-02 | 谢夫勒科技有限两合公司 | Multiple clutch device |
| CN101725645B (en) * | 2008-10-29 | 2013-10-02 | 株式会社F.C.C. | Multiple disc clutch apparatus |
| CN101725645A (en) * | 2008-10-29 | 2010-06-09 | 株式会社F.C.C. | Multiple disc clutch apparatus |
| CN102003526A (en) * | 2009-08-26 | 2011-04-06 | 通用汽车环球科技运作公司 | Actuation device having wiper seals for a dual clutch transmission |
| CN102155535A (en) * | 2009-08-26 | 2011-08-17 | 通用汽车环球科技运作有限责任公司 | Actuation device for a dual clutch transmission |
| CN102003526B (en) * | 2009-08-26 | 2014-07-16 | 通用汽车环球科技运作公司 | Actuation device having wiper seals for a dual clutch transmission |
| CN102155535B (en) * | 2009-08-26 | 2014-05-07 | 通用汽车环球科技运作有限责任公司 | Actuation device for a dual clutch transmission |
| CN103140696A (en) * | 2010-07-29 | 2013-06-05 | 舍弗勒技术股份两合公司 | Clutch device |
| CN103140696B (en) * | 2010-07-29 | 2015-11-25 | 舍弗勒技术股份两合公司 | Clutch device |
| CN103797263B (en) * | 2011-07-29 | 2016-11-23 | 现代派沃泰有限公司 | Double clutch device |
| CN103797263A (en) * | 2011-07-29 | 2014-05-14 | 现代派沃泰有限公司 | Dual Clutch Device |
| CN104053922B (en) * | 2012-01-20 | 2017-03-08 | 舍弗勒技术股份两合公司 | Wet friction clutch with integrated damper system |
| CN104053922A (en) * | 2012-01-20 | 2014-09-17 | 舍弗勒技术有限两合公司 | Wet Friction Clutch With Integrated Damping System |
| CN103591280B (en) * | 2012-08-14 | 2016-08-24 | 通用汽车环球科技运作有限责任公司 | Transmission clutch piston compensated device supply circuit |
| CN103591280A (en) * | 2012-08-14 | 2014-02-19 | 通用汽车环球科技运作有限责任公司 | Transmission clutch piston compensator feed circuit |
| CN103775533A (en) * | 2012-10-17 | 2014-05-07 | 舍弗勒技术股份两合公司 | Inline clutch with intermediate web |
| CN103775532A (en) * | 2012-10-17 | 2014-05-07 | 舍弗勒技术股份两合公司 | Inline clutch with intermediate web |
| CN103775531A (en) * | 2012-10-17 | 2014-05-07 | 舍弗勒技术股份两合公司 | Inline clutch with intermediate web |
| CN103775532B (en) * | 2012-10-17 | 2017-12-15 | 舍弗勒技术股份两合公司 | Inline clutch with intermediate web |
| CN103836091A (en) * | 2012-11-20 | 2014-06-04 | 博格华纳公司 | Dual clutch device and method for mounting the same |
| CN103836091B (en) * | 2012-11-20 | 2019-01-29 | 博格华纳公司 | Double arrangement of clutch and method for installing double arrangement of clutch |
| CN103883637A (en) * | 2012-12-20 | 2014-06-25 | 舍弗勒技术股份两合公司 | Clutch device |
| CN104033589A (en) * | 2013-03-04 | 2014-09-10 | 格特拉格传动机构和齿轮工厂赫尔曼·哈根迈尔有限公司&两合公司 | Control Method For Dual-clutch Transmission |
| CN104033589B (en) * | 2013-03-04 | 2017-01-11 | 格特拉格传动机构和齿轮工厂赫尔曼·哈根迈尔有限公司&两合公司 | Control Method For Dual-clutch Transmission |
| CN104061254A (en) * | 2013-03-21 | 2014-09-24 | 舍弗勒技术有限两合公司 | Rotation Component, Engaged Part Of Two Rotation Components And Method For Manufacturing Rotation Component |
| CN104061254B (en) * | 2013-03-21 | 2019-06-11 | 舍弗勒技术股份两合公司 | Rotating member, meshing portion of two rotating members, and method for manufacturing rotating member |
| CN105090267A (en) * | 2014-05-22 | 2015-11-25 | 舍弗勒技术股份两合公司 | Clutch assembly |
| CN105090267B (en) * | 2014-05-22 | 2019-04-30 | 舍弗勒技术股份两合公司 | clutch assembly |
| CN105526278B (en) * | 2014-10-16 | 2018-03-06 | 美国轮轴制造公司 | Piston actuator |
| CN108194533B (en) * | 2014-10-16 | 2019-09-24 | 美国轮轴制造公司 | Piston actuator |
| CN108194533A (en) * | 2014-10-16 | 2018-06-22 | 美国轮轴制造公司 | Piston actuator |
| CN105526278A (en) * | 2014-10-16 | 2016-04-27 | 美国轮轴制造公司 | Dual piston actuator |
| CN106499742A (en) * | 2015-09-03 | 2017-03-15 | 舍弗勒技术股份两合公司 | Clutch device |
| CN106499742B (en) * | 2015-09-03 | 2019-11-19 | 舍弗勒技术股份两合公司 | Clutch apparatus |
| CN107461424B (en) * | 2016-06-03 | 2019-08-23 | Fca意大利股份公司 | Motor vehicle transmission with double clutch coupling arrangement |
| CN107461424A (en) * | 2016-06-03 | 2017-12-12 | Fca意大利股份公司 | Motor vehicle transmission with double clutch coupling arrangement |
| CN109931339A (en) * | 2017-12-18 | 2019-06-25 | 舍弗勒技术股份两合公司 | Clutch device, multiple clutch device, electric drive unit and drive assembly for a motor vehicle |
| CN109931339B (en) * | 2017-12-18 | 2023-03-14 | 舍弗勒技术股份两合公司 | Clutch device, multiple clutch device, electric drive unit and drive assembly for a motor vehicle |
| CN112639321A (en) * | 2018-09-06 | 2021-04-09 | 法雷奥离合器公司 | Double clutch mechanism |
| CN112639321B (en) * | 2018-09-06 | 2024-02-13 | 法雷奥离合器公司 | Dual clutch mechanism |
| CN113544400A (en) * | 2019-05-14 | 2021-10-22 | 舍弗勒技术股份两合公司 | Clutch device, hybrid module and drive device for a motor vehicle |
| CN114096757A (en) * | 2019-07-10 | 2022-02-25 | 舍弗勒技术股份两合公司 | Actuating device for a multi-plate brake and transmission comprising an actuating device and a multi-plate brake |
Also Published As
| Publication number | Publication date |
|---|---|
| JP4722937B2 (en) | 2011-07-13 |
| JP2008519218A (en) | 2008-06-05 |
| WO2006048179A1 (en) | 2006-05-11 |
| DE102004055361A1 (en) | 2006-05-18 |
| US7648012B2 (en) | 2010-01-19 |
| DE502005007588D1 (en) | 2009-08-06 |
| EP1807636A1 (en) | 2007-07-18 |
| DE102004055361B4 (en) | 2008-10-30 |
| US20070256907A1 (en) | 2007-11-08 |
| CN101052819B (en) | 2010-07-28 |
| EP1807636B1 (en) | 2009-06-24 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101052819A (en) | Dual-action clutch system | |
| US9568069B2 (en) | Transmission for a motor vehicle | |
| US7485061B2 (en) | Drive train of hybrid vehicle | |
| CN106246815B (en) | Double-speed active transfer case | |
| US20070240961A1 (en) | Dual clutch arrangement for a dual clutch transmission | |
| JP6525024B2 (en) | Transmission brake system | |
| CN103228954A (en) | Vehicular power transmission device | |
| CN107202079A (en) | Hydraulic control system for wet-type dual-clutch | |
| CN101061333A (en) | Vehicular automatic transmission | |
| CN1772524A (en) | Vehicular drive system | |
| CN107202081A (en) | It is supported on the wet-type dual-clutch in its control system | |
| US8397595B2 (en) | Drive unit for a motor vehicle | |
| CN1712265A (en) | Torque transmitting unit | |
| CN101048608A (en) | Forward-reverse switching device for stepless speed changer | |
| CN110290958A (en) | Multiple clutch device and hybrid module for a motor vehicle | |
| CN103228955A (en) | Vehicular power transmission device | |
| CN103228956A (en) | Vehicular power transmission device | |
| CN1712757A (en) | Fixed pulley assembly with start-up clutch and torque sensing device | |
| US9518636B2 (en) | Transmission for a motor vehicle | |
| KR20120013298A (en) | Driving mechanism for a vehicle | |
| CN1795340A (en) | Planetary gear train | |
| KR20180040684A (en) | Clutch device for hybrid drive system | |
| CN104895949A (en) | Double clutch structure | |
| US8409041B2 (en) | Pump cover inlet porting and seal for hybrid transmission | |
| CN1178806C (en) | Gearing system for small sized vehicle |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant |